High-stability bearing bed for warp knitting machine and method

Abstract

The present application relates to the field of textile machinery and damping control, specifically to a warp knitting machine high-stability bearing seat and a method thereof; comprising a bearing main frame, a damping energy dissipation core, a leveling support foot, a spherical self-adaptive pad, a monitoring part and a controller; the system obtains top and bottom end vibration data in real time through a sensor, calculates vibration transmission rate and attenuation rate and then solves dynamic stiffness, thereby evaluating damping aging state and calculating resonance critical speed; the core is to densely fill the damping energy dissipation core in the main frame to dissipate periodic excitation energy generated by high-speed operation, and to use spherical contact matching of the hemispherical protrusion at the bottom of the support foot and the hemispherical groove of the spherical self-adaptive pad, so that the support foot can be freely deflected to adaptively compensate uneven ground; the present application solves the problems of insufficient existing foundation stiffness and obvious high-frequency vibration transmission, effectively avoids long-term stress concentration and loose connection of the rack, and greatly improves the support stability.

Description

Technical Field

[0001] This invention relates to the field of textile machinery and vibration control, specifically to a high-stability bearing base for warp knitting machines and its method. Background Technology

[0002] Under continuous high-speed operation of a warp knitting machine, the main equipment periodically generates strong alternating excitation forces, and this dynamic load is directly transmitted along the frame to the foundation. To support such high-speed equipment, existing solutions generally adopt an integral cast base or a common welded base system, that is, the static load and dynamic load of the main equipment are directly supported by a rigid metal frame. Although this solution has a certain load-bearing capacity in static support scenarios, due to the lack of an effective damping energy dissipation mechanism within its structure, the overall dynamic stiffness is insufficient, and the attenuation of high-frequency excitation along the metal path is minimal, resulting in obvious vibration transmission. At the same time, in complex workshop floor environments, the existing base support structure is difficult to adaptively adjust its spatial posture, and is prone to introducing additional bending stress due to uneven foundation or installation errors. Under long-term high-frequency vibration, this can frequently lead to loosening of the foundation structure or even local fatigue damage. In addition, existing purely mechanical bases lack a design that senses the vibration transmission path and cannot obtain the vibration response characteristics of the top and bottom without stopping the machine, making it difficult to provide quantitative data support for resonance avoidance and structural aging assessment of the equipment.

[0003] Therefore, how to improve the vibration reduction and energy dissipation and adaptive leveling performance of the base bearing structure, and realize the real-time monitoring of the structural vibration state and dynamic stiffness assessment, has become an urgent technical problem to be solved. Summary of the Invention

[0004] To solve the above-mentioned technical problems, the present invention provides a high-stability support base for warp knitting machines and a method thereof. Specifically, the technical solution of the present invention is as follows: A high-stability support base for a warp knitting machine, comprising: The main support frame has an upper mounting plate on top. The internal structure of the main support frame has a damping filling cavity. The upper mounting plate is used to fix external machinery and equipment. The damping energy dissipation core is densely injected into the damping filling cavity; The leveling support foot is connected to the bottom of the main support frame, and the bottom end of the leveling support foot is provided with a hemispherical protrusion; A spherical adaptive pad is placed on the ground. The upper surface of the spherical adaptive pad is provided with a hemispherical groove that matches the hemispherical protrusion. The hemispherical protrusion is located in the hemispherical groove to form a spherical contact fit. Two monitoring units are respectively installed on the upper mounting plate and the spherical adaptive pad. Each monitoring unit is equipped with an acceleration sensor. The two acceleration sensors are used to acquire a first vibration electrical signal characterizing the top vibration acceleration in the vertical direction and a second vibration electrical signal characterizing the bottom vibration acceleration in the vertical direction. The controller, electrically connected to the two acceleration sensors, is used to receive the vibration electrical signals and control the acceleration sensors.

[0005] In one embodiment, the supporting main frame is a hollow square steel column with a wall thickness of 10mm and a cross-sectional dimension of 200mm×200mm. The upper mounting plate has through holes for fixing external machinery and equipment with bolts.

[0006] In one embodiment, a base plate is fixedly connected to the bottom end face of the main support frame, and an internal threaded hole is machined in the center of the base plate. The top of the leveling support foot is a screw, which is screwed into the internal threaded hole.

[0007] In one embodiment, the damping energy-dissipating core is formed by curing a mixture of epoxy resin and quartz sand in a volume ratio of 1:3.

[0008] In one embodiment, the surfaces of both the hemispherical protrusion and the hemispherical groove are hardened and coated with molybdenum disulfide grease.

[0009] In one embodiment, the cooperation between the hemispherical protrusion and the hemispherical groove allows the leveling support foot to deflect freely within a spatial cone angle range of ±5 degrees.

[0010] Methods for establishing a high-stability support base for warp knitting machines include: S1. Acquire the first vibration electrical signal of the acceleration sensor on the upper mounting plate in real time, and calculate the peak value of the top vibration acceleration; S2. Obtain the second vibration electrical signal of the acceleration sensor on the spherical adaptive pad, and calculate the peak value of the bottom vibration acceleration; S3. Based on the peak value of the bottom vibration acceleration and the peak value of the top vibration acceleration, and combined with the preset structural equivalent stiffness coefficient, real-time dynamic stiffness data is obtained. S4. Based on the real-time dynamic stiffness data, conduct a safety assessment of the aging state of the damping energy dissipation core or the resonance risk of the bearing base.

[0011] In one embodiment, step S4 involves a safety assessment of the aging state of the damping energy dissipation core based on the real-time dynamic stiffness data, specifically including: S601. Obtain the standard dynamic stiffness under the initial installation state, and obtain the stiffness difference based on the standard dynamic stiffness and the real-time dynamic stiffness data; S602. Obtain a preset time interval and obtain average degradation data based on the stiffness difference over a continuous time period. S603. Based on the stiffness difference and the average degradation data, obtain the aging score of the damping energy dissipation core, and output the aging warning status based on the preset aging threshold range.

[0012] In one embodiment, step S4 involves a safety assessment of the resonance risk of the load-bearing base based on the real-time dynamic stiffness data, specifically including: S701. Obtain the total equivalent mass of the bearing base and external machinery and equipment in real time, and calculate the actual natural frequency based on the real-time dynamic stiffness data; S702. Obtain a preset rotational speed conversion coefficient and convert the actual natural frequency to obtain the resonance critical rotational speed; S703. The current operating speed of the rotating spindle installed in the external machine equipment is obtained in real time, and the real-time speed difference is obtained based on the operating speed and the resonance critical speed.

[0013] In one embodiment, the main support frame is further provided with a speed regulation module, which, controlled by the controller, allows for controlled adjustment of the rotating spindle. Step S703 is followed by: S801. Calculate the initial excitation energy based on the peak value of the top vibration acceleration; S802. Obtain the vibration electrical signals of the two acceleration sensors and recalculate the real-time speed difference. Obtain the absolute value corresponding to the real-time speed difference as a safety margin feature. S803. Evaluate the safety status of the damping energy dissipation core on the main support frame based on the initial excitation energy and the safety margin characteristics, and output the corresponding safety status result.

[0014] The present invention has the following beneficial effects: 1. This invention effectively dissipates the periodic excitation energy generated by the high-speed operation of the warp knitting machine by densely filling the damping cavity inside the main support frame with a damping energy-dissipating core; at the same time, the hemispherical protrusion at the bottom of the leveling support foot and the hemispherical groove of the spherical adaptive pad form a spherical contact fit, allowing the leveling support foot to freely deflect to adaptively compensate for uneven ground; this structure fundamentally solves the problems of insufficient rigidity of existing foundations and obvious high-frequency vibration transmission, effectively avoids long-term frame stress concentration and loosening of connections, and greatly improves support stability; 2. This invention sets up monitoring units on the top mounting plate and the bottom spherical adaptive pad, respectively. The controller synchronously acquires the vertical vibration acceleration of the top and bottom through acceleration sensors at both ends. This method can calculate the vibration transmissibility and directly convert it into real-time attenuation rate and real-time dynamic stiffness data without stopping the equipment. This makes up for the lack of dynamic monitoring in traditional equipment. It can not only accurately evaluate the aging and safety status of the damping energy dissipation core online, but also effectively realize resonance early warning. Attached Figure Description

[0015] Figure 1 This is a schematic diagram of the overall structure of the device; Figure 2 This is a schematic diagram of the main support frame structure of the device; Figure 3 This is a schematic diagram of the cross-sectional structure of the damping filling cavity of the device; Figure 4 This is a schematic diagram of the spherical adaptive pad structure of the device; Figure 5 This is a flowchart of the method of the present invention.

[0016] In the diagram: 1. Main support frame; 2. Upper mounting plate; 3. Damping filling cavity; 4. External machinery and equipment; 5. Damping energy dissipation core; 6. Leveling support foot; 7. Hemispherical protrusion; 8. Spherical self-adaptive pad; 9. Hemispherical groove; 10. Monitoring unit; 11. Accelerometer; 12. Controller; 13. Hollow square steel column; 14. Through hole; 15. Bolt; 16. Base plate; 17. Internal threaded hole; 18. Screw; 19. Rotary spindle; 20. Speed ​​control module; 21. Molybdenum disulfide grease. Detailed Implementation

[0017] The technical solutions in the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the scope of protection of this application. Example 1:

[0018] Combination Figure 1 As shown, the high-stability support base for a warp knitting machine includes: The main frame 1 is supported by an upper mounting plate 2 on top. The internal structure of the main frame 1 has a damping filling cavity 3. The upper mounting plate 2 is used to fix external machinery and equipment 4. The damping energy dissipation core 5 is densely injected into the damping filling cavity 3; The leveling support foot 6 is connected to the bottom of the main support frame 1, and the bottom end of the leveling support foot 6 is provided with a hemispherical protrusion 7; A spherical self-adaptive pad 8 is placed on the ground. The upper surface of the spherical self-adaptive pad 8 is provided with a hemispherical groove 9 that matches the hemispherical protrusion 7. The hemispherical protrusion 7 is located in the hemispherical groove 9 to form a spherical contact fit. Two monitoring units 10 are respectively installed on the upper mounting plate 2 and the spherical adaptive pad 8. Each monitoring unit 10 is equipped with an acceleration sensor 11. The two acceleration sensors 11 are used to acquire a first vibration electrical signal characterizing the top vibration acceleration in the vertical direction and a second vibration electrical signal characterizing the bottom vibration acceleration in the vertical direction. The controller 12 is electrically connected to two acceleration sensors 11 and is used to receive vibration electrical signals and control the acceleration sensors 11. When the warp knitting machine is running at high speed, the excitation force of the main machine is transmitted to the foundation through the frame. Traditional integral cast bases or ordinary welded bases are prone to problems such as insufficient dynamic stiffness, obvious vibration transmission and loose foundation. To solve this problem, this embodiment sets the main load-bearing frame 1 as the main load-bearing component. The top of the main load-bearing frame 1 is fixed with an upper mounting plate 2, which is used to connect with the base of the warp knitting machine main machine so that the static load and periodic excitation load of the main machine are input into the main load-bearing frame 1. A damping filling cavity 3 is formed inside the main frame 1. The damping filling cavity 3 is densely filled with a damping energy dissipation core 5. When subjected to compression waves and tensile waves, the damping energy dissipation core 5 reduces the vibration transmission rate through internal material interface friction, micro-slip and viscoelastic dissipation, thereby improving the attenuation capability of the base for high-frequency excitation. The bottom of the main frame 1 is connected to the leveling support foot 6. The bottom of the leveling support foot 6 is provided with a hemispherical protrusion 7. The spherical adaptive pad 8 is placed on the ground and its upper surface is provided with a hemispherical groove 9. The hemispherical protrusion 7 is located in the hemispherical groove 9 to form a spherical contact fit, thereby allowing the base to adaptively adjust its posture at a small angle with the ground, reducing the additional bending moment caused by uneven ground. Two monitoring units 10 are respectively arranged on the upper mounting plate 2 and the spherical adaptive pad 8, and are used to collect vibration signals at the input and output ends of the vibration path. The acceleration sensor 11 in the monitoring unit 10 is preferably an industrial-grade piezoelectric or microelectromechanical system type single-axis acceleration sensor 11. The sensor's sensitive axis is arranged in the vertical direction. The acceleration sensor 11 on the upper mounting plate 2 outputs the top vibration acceleration signal, and the acceleration sensor 11 on the spherical adaptive pad 8 outputs the bottom vibration acceleration signal. The controller 12 is electrically connected to two acceleration sensors 11. The controller 12 is used for power supply, sampling, filtering, peak extraction and processing, so that the base not only has a load-bearing and vibration-damping structure, but also has the ability to sense its own vibration transmission state in real time. The technical effect of this structural solution is that the mechanical vibration damping unit and the vibration monitoring unit are arranged correspondingly on the same load-bearing path. The controller 12 can directly reflect the vibration transmission change of the base based on the top vibration acceleration and bottom vibration acceleration, providing measurable data for subsequent dynamic stiffness assessment and speed adjustment.

[0019] Combination Figure 2 As shown, the main support frame 1 is a hollow square steel column 13 with a wall thickness of 10mm. The cross-sectional dimensions of the hollow square steel column 13 are 200mm×200mm. The upper mounting plate 2 has through holes 14 for fixing and connecting external machinery and equipment 4 with bolts 15. To ensure that the main support frame 1 can balance load-bearing capacity, welding feasibility, and damping filling space, the main support frame 1 is made of hollow square steel column 13 made of low alloy high-strength structural steel with a yield strength of 345MPa, with a wall thickness of 10mm and a cross-sectional size of 200mm×200mm. This size combination ensures that the square steel column has sufficient moment of inertia when bearing the self-weight of the warp knitting machine and the periodic alternating load, while leaving a continuous cavity inside to facilitate the formation of a stable damping filling cavity 3. If the wall thickness is less than 10mm, the column is prone to local wall bulging and welding heat-affected zone fatigue under long-term high-frequency vibration; if the wall thickness is greater than 10mm, the self-weight of the machine base increases, the material utilization rate decreases, resulting in an increase in the overall structural load of the machine base, which increases the difficulty of subsequent handling and assembly operations; the upper mounting plate 2 is welded to the top end face of the hollow square steel column 13. The upper mounting plate 2 is preferably made of thick steel plate, and through holes 14 are provided on its surface. The through holes 14 are used to pass through high-strength bolts 15 and connect to the base of the external machine equipment 4. Four through holes 14 can be set and distributed at the four corners of the upper mounting plate 2, corresponding to the connection holes on the base of the warp knitting machine main unit. The main unit and the base are rigidly fixed by the pre-tightening force of the bolts 15, so that the main unit's excitation load is stably input into the main frame 1. The technical significance of using hollow square steel columns 13 instead of solid metal columns is that the hollow structure simultaneously undertakes the functions of load bearing and accommodating damping materials. The structural path is short, the load transmission direction is clear, and the top and bottom vibration accelerations collected by the controller 12 can better correspond to the vertical vibration transmission characteristics of the base body.

[0020] Combination Figure 3 As shown, a base plate 16 is fixedly connected to the bottom end face of the main support frame 1. An internal threaded hole 17 is machined in the center of the base plate 16. The top of the leveling support foot 6 is a screw 18, which is screwed into the internal threaded hole 17. To achieve height adjustment of the base and ensure a reliable axial force path between the leveling support foot 6 and the main support frame 1, a base plate 16 is fixedly installed on the bottom end face of the main support frame 1. The base plate 16 is preferably a thick steel plate and is welded circumferentially to the hollow square steel column 13. An internal threaded hole 17 is machined in the center of the base plate 16. A screw 18 that matches the top of the leveling support foot 6 is installed. The screw 18 is screwed into the internal threaded hole 17 to form an adjustable threaded connection. The threaded connection allows the height of the main support frame 1 off the ground to be changed by rotating the leveling support foot 6 to compensate for the height difference in the workshop floor and to make the upper mounting plate 2 reach the set level; the base plate 16 is set on the bottom end face of the main support frame 1 to evenly transfer the axial load from the column to the area around the internal threaded hole 17, reducing local stress concentration. The technical advantage of threaded connection is that it allows for height adjustment at the millimeter level during installation, which facilitates leveling of the entire warp knitting machine. With the spherical contact structure, the screw 18 mainly bears the axial load, reducing the additional bending moment and decreasing the probability of abnormal wear of the threaded pair under high-frequency vibration. This structure makes the main support frame 1, the base plate 16, the internal threaded hole 17 and the leveling support foot 6 form a continuous force chain, which helps to maintain the long-term load-bearing stability of the machine base.

[0021] The damping energy dissipation core 5 is composed of a mixture of epoxy resin and quartz sand with a volume ratio of 1:3, which is then cured. The damping energy dissipation core 5 is formed by curing a mixture of epoxy resin and quartz sand with a volume ratio of 1:3, wherein the epoxy resin is the continuous phase and the quartz sand is the dispersed particulate phase; this ratio takes into account the casting fluidity, the overall strength after curing and the vibration energy dissipation capacity. After curing, epoxy resin can form a bonding interface with the inner wall of the main support frame 1, so that the damping energy dissipation core 5 and the hollow square steel column 13 share the force. Since the volume ratio of quartz sand particles is larger than that of epoxy resin matrix, the particles inside the material and the resin interface generate micro-scale relative displacement and interface friction under alternating stress, which can convert some mechanical vibration energy into heat release, thereby reducing the vibration amplitude transmitted from the upper mounting plate 2 to the bottom spherical adaptive pad 8. During implementation, epoxy resin and curing agent can be premixed and then dry quartz sand can be added, stirred evenly and poured into the damping filling cavity 3. During the pouring process, no obvious voids are controlled. After curing, a dense entity is formed. The reason for using this material instead of a single resin or a single metal filler is that a single resin has a low compressive modulus, which limits its long-term load-bearing stability; while a single metal filler improves quality, it is difficult to form an effective internal energy dissipation interface; the epoxy resin and quartz sand mixed curing structure has both compressive support and damping energy dissipation functions when bearing warp knitting machine loads, and can directly support the implementation of methods based on attenuation rate and dynamic stiffness.

[0022] Combination Figure 4 As shown, it is coated with molybdenum disulfide grease 21; The hemispherical protrusion 7 at the bottom of the leveling support foot 6 and the hemispherical groove 9 on the spherical self-adaptive pad 8 form a spherical contact pair. This contact pair needs to maintain deflection capability while bearing the load of the whole machine, so its surface condition directly affects the contact stability and service life. In order to reduce indentation wear, adhesive wear and fretting wear under long-term pressure contact, the surfaces of the hemispherical protrusion 7 and the hemispherical groove 9 are both hardened to increase the surface hardness and enhance the resistance to contact fatigue. After quenching, molybdenum disulfide grease 21 is applied to the mating surfaces of both surfaces. The solid lubrication properties of molybdenum disulfide reduce the coefficient of friction of the spherical contact and reduce the resistance caused by small angle compensation after leveling. The technical effect of this treatment is that the spherical contact pair can still maintain relatively stable mating accuracy under long-term vibration environment, and avoid the loss of self-adaptive ability of the spherical mating due to surface seizing. Because the spherical fit remains in good condition, the lateral constraint on the main support frame 1 is reduced, and the torsional interference component in the top vibration acceleration signal collected at the upper mounting plate 2 and the bottom vibration acceleration signal collected at the spherical adaptive pad 8 is reduced accordingly, which is beneficial for the controller 12 to accurately calculate the vibration transmission rate.

[0023] The combination of the hemispherical protrusion 7 and the hemispherical groove 9 allows the leveling support foot 6 to deflect freely within a spatial cone angle range of plus or minus five degrees; Considering the construction errors, floor settlement, and local tilt of the foundation in the workshop, the spherical contact pair is designed to allow the leveling support foot 6 to deflect freely within a spatial cone angle range of ±5 degrees. Free deflection means that the axis of the leveling support foot 6 can be compensated for its posture within five degrees relative to the normal direction of the spherical adaptive pad 8 without producing obvious edge jamming. This angle range covers common installation deviations on industrial floors and avoids excessive deflection angles that could reduce the spherical contact area and increase contact stress. During implementation, the curvature radius of the hemispherical protrusion 7 and the hemispherical groove 9 are matched, and a clearance is reserved to meet the above-mentioned five-degree deflection angle, so that the leveling support foot 6 still has limited deflection capability under load. This design makes the main support frame 1 closer to the axial compression and tension state in actual installation, reducing the additional bending stress and torsional load introduced by uneven ground. The corresponding technical effect is that the natural frequency of the base is less affected by the foundation installation error, the stability of the vertical vibration data collected by the monitoring unit 10 is improved, and the data fluctuation range can be controlled within the processable range when calculating the attenuation rate, dynamic stiffness and resonance critical speed based on the top vibration acceleration and bottom vibration acceleration. Example 2:

[0024] Please see Figure 5 A method for providing a high-stability support base for a warp knitting machine includes: S1. Acquire the first vibration electrical signal of the acceleration sensor 11 on the upper mounting plate 2 in real time, and calculate the peak value of the top vibration acceleration; S2. Obtain the second vibration electrical signal of the accelerometer 11 on the spherical adaptive pad 8, and calculate the peak value of the bottom vibration acceleration; S3. Based on the peak value of the bottom vibration acceleration and the peak value of the top vibration acceleration, and combined with the preset structural equivalent stiffness coefficient, real-time dynamic stiffness data is obtained. S4. Based on real-time dynamic stiffness data, conduct a safety assessment of the aging state of the damping energy dissipation core 5 or the resonance risk of the bearing base. This method is applied to the bearing base to convert the structural vibration response into calculable dynamic stiffness parameters. In S1, the controller 12 receives the first vibration electrical signal, which is a characteristic of the top vibration acceleration, output by the accelerometer 11 on the upper mounting plate 2 at a set sampling frequency. The first vibration electrical signal is an electrical signal of the vertical acceleration of the upper mounting plate 2 changing with time. The controller 12 performs analog-to-digital conversion, bandpass filtering, and period division on the electrical signal, and extracts the peak value of the top vibration acceleration within a continuous set period. The set period can be 10 consecutive main vibration periods, and the peak value can be the point of maximum absolute value or the average value of multiple period peak values. In S2, the controller 12 synchronously acquires the second vibration electrical signal representing the bottom vibration acceleration output by the acceleration sensor 11 on the spherical adaptive pad 8, and calculates the bottom vibration acceleration peak value using the same sampling and filtering strategy as in S1. In S3, the controller 12 divides the peak value of the bottom vibration acceleration by the peak value of the top vibration acceleration to obtain the vibration transmissibility; in the effective vibration isolation section where the transmissibility is determined to be less than 1, the real-time attenuation rate is obtained by subtracting the vibration transmissibility from 1. The preset structural equivalent stiffness conversion parameters are called, and the real-time attenuation rate is multiplied by the preset structural equivalent stiffness coefficient to obtain the real-time dynamic stiffness data; the preset coefficient is calibrated by the base geometry, material density and mode shape participating mass during the installation and commissioning phase. The specific calibration conversion logic is as follows: calculate the theoretical mass of the main frame 1 based on the geometric dimensions and material density of the base, extract the modal participation mass within the working frequency band of the base using finite element modal analysis, obtain the main mechanical resonance frequency based on the rated speed of the warp knitting machine or extracted by finite element modal analysis as the preset reference angular frequency, multiply the modal participation mass by the square of the preset reference angular frequency to obtain the basic stiffness value with stiffness dimension, and this basic stiffness value is used as the structural equivalent stiffness coefficient; This coefficient is essentially a mapping reference value connecting the dimensionless attenuation rate and the actual dynamic stiffness; specifically, the structural equivalent stiffness conversion essentially constitutes a dynamic stiffness mapping model; the purpose of this model is to accurately estimate the real-time dynamic stiffness parameters of the entire base under operating conditions where static loading measurements cannot be directly performed. In terms of logical structure and data flow, the model receives the real-time attenuation rate as a dynamic input reflecting energy dissipation, and reads the equivalent stiffness coefficient composed of the base geometry, material density, and mode mass as a static structural input. The model multiplies the dynamic input and static input to output real-time dynamic stiffness data. In terms of physical relationships, the model simulates the coupling physical relationship between the dynamic stiffness of the damping energy dissipation core 5 and the main support frame 1 under alternating loads and the vibration energy dissipation ratio and structural inertial mass of the system. Since the change in the structural attenuation rate directly reflects the change in the stiffness characteristics of the internal materials, the model can convert the dimensionless attenuation rate into a stiffness value with practical engineering significance. The technical significance of this method is that it can obtain dynamic stiffness data related to the structural health status by utilizing the vibration response of the top and bottom during operation without disassembling the base or conducting static loading tests, thereby providing real-time basis for resonance judgment. To ensure the traceability of the calculation and derivation process of vibration transmissibility and real-time dynamic stiffness data, the processing sequence of controller 12 in S1 to S4 is preferably defined as follows: First, zero-point calibration is performed on the two original acceleration electrical signals at the top and bottom to eliminate sensor installation bias; then, bandpass filtering is performed according to the main excitation frequency band corresponding to the current operating speed of the warp knitting machine, preferably retaining the main excitation frequency and its adjacent narrowband components to suppress random ground impacts and electrical noise; Then, peak values ​​of the top and bottom signals are extracted using the same time window. The preferred time window is 10 consecutive main vibration cycles or a fixed duration of 1 to 3 seconds to ensure that the two peak values ​​originate from the same operating state. Regarding the step in S3 of obtaining the ratio of the bottom vibration acceleration peak value to the top vibration acceleration peak value, the specific formula for calculating the vibration transmissibility in this embodiment is as follows: ; in, For vibration transmissibility, This represents the peak value of the bottom vibration acceleration. The peak value of the top vibration acceleration is used because the top position is closer to the excitation input end and the bottom position is closer to the foundation output end. The ratio of the bottom peak value to the top peak value can directly represent the proportion of vibration transmitted to the ground. To ensure calculation stability, when the peak value of the top vibration acceleration is lower than the preset minimum effective value, the controller 12 determines that the current period is a period of low excitation or no-load disturbance, suspends the update of vibration transmissibility, and only maintains the previous effective calculation result, thereby avoiding abnormal ratio calculation due to the denominator being lower than the set lower limit threshold. The specific setting benchmark for the preset minimum effective value is: after the base and external machine equipment 4 are installed, take 1.1 to 1.2 times the upper limit of the peak value of the top vibration acceleration measured when the drive motor of the external machine equipment 4 is in no-load idle running state as the preset minimum effective value. The physical meaning of the real-time attenuation rate is the attenuation capability of the base to the main vibration channel under the current operating state. The larger the value, the more vibration energy the base will dissipate inside the main support frame 1 and the damping energy dissipation core 5. The smaller the value, the higher the proportion of vibration transmitted to the foundation. The preset equivalent stiffness conversion is not an arbitrary empirical value, but is obtained through calibration during the installation and commissioning phase: first, the peak value of the top vibration acceleration, the peak value of the bottom vibration acceleration, and the corresponding base response data are collected at at least two known operating speed points; then, combined with the geometric dimensions of the base, material density, and the installation quality of the external machinery and equipment 4, a correspondence between the real-time attenuation rate and the dynamic stiffness is established; when the controller 12 is running, it preferably outputs the real-time dynamic stiffness data by looking up a table or by piecewise linear interpolation. The purpose of this stepwise conversion method is to first convert directly measurable acceleration metrics into vibration transmissibility, then into real-time attenuation rate, and finally into real-time dynamic stiffness data, so that each processing result has a clear input source, physical meaning, and subsequent use. Among them, real-time dynamic stiffness data serves as the basic input for subsequent aging evaluation, natural frequency calculation, and speed regulation judgment. To ensure the dynamic stiffness mapping model has clear programmability and clearly demonstrates the data flow process, a quantitative derivation example is provided here: Assume that in the initial calibration stage, the equivalent stiffness coefficient of the structure determined by the geometric dimensions and material density is 2000 N / mm; at a certain operating moment, the controller 12 extracts the peak value through steps S1 and S2, and calculates the real-time attenuation rate of 0.35 in step S3. In the final mapping calculation of step S3, the controller 12 directly multiplies the real-time attenuation rate of 0.35 with the equivalent stiffness coefficient of 2000 N / mm by the calibration value, and outputs the real-time dynamic stiffness data as 700 N / mm. The calculation result is stored in the register of the controller 12 as the basic input data for subsequent evaluation of aging state and resonance risk, thereby ensuring that the data flow logic from the acquisition end to the calculation end and then to the application end is clear and closed-loop.

[0025] In S4, based on real-time dynamic stiffness data, a safety assessment of the aging state of the damping energy dissipation core 5 is conducted, specifically including: S601. Obtain the standard dynamic stiffness under the initial installation state, and obtain the stiffness difference based on the standard dynamic stiffness and real-time dynamic stiffness data; S602. Obtain a preset time interval and obtain average degradation data based on the stiffness difference over a continuous time period. S603. Based on the stiffness difference and average degradation data, the aging score of the damping energy dissipation core 5 is obtained, and the aging warning status is output based on the preset aging threshold range. After obtaining the real-time dynamic stiffness data, this embodiment further evaluates the health status of the base; in S601, the controller 12 reads the standard dynamic stiffness in the initial installation state. The standard dynamic stiffness is a reference value obtained and stored through the same sampling and calculation process when the base is installed, leveled and the damping energy dissipation core 5 is in the initial health state. The controller 12 subtracts the current real-time dynamic stiffness data from the standard dynamic stiffness to obtain the stiffness difference value. An increase in the stiffness difference value indicates that the equivalent stiffness of the base has decreased, which may be due to micro-cracks or debonding inside the damping energy dissipation core 5, or changes in the force path caused by micro-loosening of the threaded pair of the leveling support foot 6. In S602, the controller 12 statistically analyzes the stiffness difference over multiple consecutive time periods at set time intervals. The set time interval can be set to one minute, five minutes, or longer depending on the machine's speed stability and sampling capability. The average degradation data is obtained by averaging the stiffness difference within this time interval. The average degradation data is used to suppress short-term fluctuations caused by instantaneous impacts, random disturbances in the workshop, and occasional loads. In S603, the controller 12 calculates the ratio between the stiffness difference and the average degradation data, and combines the ratio with the average degradation data according to a preset weight to output the aging evaluation result of the damping energy dissipation core 5. The weighting method can be set so that the ratio reflects the degree of abrupt change and the average degradation data reflects the degree of cumulative decay. Both are used together to distinguish between short-term anomalies and continuous aging. In this process, step S603 actually constructs an aging state assessment model; the purpose of this model is to accurately identify the true degree of health degradation of the damping energy dissipation core 5 under complex workshop disturbances; in terms of logical structure and data flow, the model contains two parallel feature extraction branches: one branch receives the ratio of stiffness difference to average degradation data as input to extract abrupt features; the other branch receives average degradation data as input to extract long-term cumulative decay features. The model integrates these two features with preset weights and outputs the final aging state evaluation result. In terms of the physical relationship represented, the model as a whole represents the dual failure mechanism of damping materials under long-term mechanical fatigue, namely progressive damage and sudden failure. Because the model integrates short-term mutations and long-term decay trends, it can effectively filter random disturbances and provide accurate aging warnings. The technical advantage of this evaluation method is that it can not only identify the result of the decrease in frame stiffness, but also determine whether the damping energy dissipation core 5 has entered the aging stage by combining the persistence and rate of change of the decrease, thereby providing a quantitative basis for maintenance arrangements. The preferred method for determining the standard dynamic stiffness is as follows: under the rated load condition after initial installation, select a stable working condition within the commonly used operating speed range of the warp knitting machine, continuously collect multiple sets of real-time dynamic stiffness data, and take the average value of these multiple sets of data as the standard dynamic stiffness to avoid accidental deviations in a single measurement. The standard dynamic stiffness serves as a health reference benchmark in subsequent use. Its logical function is to characterize the benchmark stiffness level that the base should have when the damping energy dissipation core 5 is not aged and the connecting parts are not loose. The stiffness difference obtained by S601 is the deviation of the current state from the benchmark state. The larger the deviation, the more obvious the degradation of the base bearing path and damping unit relative to the initial state. The time interval set in S602 is preferably selected based on the stability of the working conditions; when the speed fluctuation of the warp knitting machine is lower than the preset speed deviation threshold and the load remains constant, the first time interval can be used to improve the response speed; the preset speed deviation threshold is obtained based on the statistical analysis of the historical extreme values ​​of speed fluctuation of the warp knitting machine under no-load and full-load conditions, and is preferably set to ±2% of the rated speed; When the operating conditions change frequently, a second time interval greater than the first time interval can be taken to enhance statistical stability; the physical meaning of the average degradation data is the average level of stiffness decrease over a continuous time range, and its role is to reflect whether the degradation of the damping energy dissipation core 5 is continuous, rather than just an instantaneous anomaly. The ratio term in S603 is used to reflect the degree of deviation of the current stiffness difference from the continuous degradation level: the preset ratio threshold is set based on the statistical data of the historical durability fatigue test of the base, and its preferred range is set to 1.5 to 2.0; if it exceeds the preset ratio threshold, it indicates that there is a degradation mutation greater than the average degradation data at the current moment. If the ratio is close to one, it means that the current degradation trend is basically consistent with the existing degradation trend; when the ratio exceeds the preset ratio threshold, the aging warning state is directly triggered and the subsequent aging comprehensive scoring judgment process based on weighted calculation is no longer executed. To avoid abnormal amplification of the ratio due to excessively small average degradation data, the controller 12 preferably sets a minimum calculation base value, which is preferably set to 3% to 5% of the standard dynamic stiffness. When the average degradation data is lower than this minimum calculation base value, the controller 12 determines that the period is in the basic healthy and stable range, determines that the current aging state is normal, and skips the subsequent aging comprehensive score calculation process based on the ratio. The preset weights are determined during the installation and commissioning phase in conjunction with historical test samples. The ratio weight is used to enhance the sensitivity to rapid anomalies such as sudden debonding and local cracking, while the average degradation data weight is used to enhance the ability to identify gradual anomalies such as long-term aging and slow loosening. The controller 12 can output at least three levels of aging status based on the weighted result: when the weighted result is in the low level range, it is evaluated as normal status; when the weighted result enters the middle range, it is evaluated as attention status, prompting a re-inspection; when the weighted result enters the high level range, it is evaluated as aging warning status, prompting maintenance or replacement of the damping energy dissipation core 5 and the connection parts. The above-mentioned interval boundaries are preferably obtained through joint calibration of prototype durability tests, aging disassembly results, and field operation records, so that the aging evaluation results have a clear calculation source and can correspond to actual maintenance decisions; Specifically, the weighted combination logic can be programmed as follows: the controller 12 internally sets the aging score calculation rules, that is, the aging score is equal to the first weight multiplied by the ratio, plus the second weight multiplied by the average degradation data; wherein, the first weight has the same preset dimension as the aging score, and the second weight has a conversion coefficient to convert the rigid dimension of the average degradation data into the dimension of the aging score. For example, the first weight is set to 0.4 to capture sudden changes, and the second weight is set to 0.6 to measure long-term degradation. Assuming that the stiffness difference measured in a certain period is 50 N / mm and the average degradation data is 40 N / mm, the ratio is 1.25. The controller 12 calculates the aging score as 0.4 multiplied by 1.25 plus 0.6 multiplied by 40, which equals 24.5. The controller 12 compares the aging score with a preset threshold. If the aging score is below 20, it is considered to be in a normal state; if it is between 20 and 40, it is considered to be in a state of concern; and if it is above 40, it is considered to be in an aging warning state. Through this clear weighting and threshold determination, the abstract aging state evaluation is transformed into a numerical calculation that can be directly executed by the software code, avoiding the problem of missing internal calculation logic.

[0026] In S4, a safety assessment of the resonance risk of the bearing base is conducted based on real-time dynamic stiffness data, specifically including: S701. The total equivalent mass of the bearing base and the external machine equipment 4 is obtained in real time, and the actual natural frequency is calculated based on the real-time dynamic stiffness data. S702. Obtain the preset speed conversion coefficient and convert the actual natural frequency to obtain the resonance critical speed. S703. The current operating speed of the rotating spindle 19 installed in the external machine equipment 4 is obtained in real time, and the real-time speed difference is obtained based on the operating speed and the resonance critical speed. In this embodiment, after obtaining real-time dynamic stiffness data, the resonance risk of the warp knitting machine system is judged in real time. In S701, the controller 12 obtains the total equivalent mass of the bearing base and the external machine equipment 4. The total equivalent mass includes the equivalent mass of the bearing base participating in the vibration and the equivalent mass of the warp knitting machine main unit participating in the vibration. This total equivalent mass can be a fixed value input during the installation and commissioning stage, or it can be obtained by the controller 12 calling the equipment configuration parameter table. The controller 12 calculates the actual natural frequency based on the real-time dynamic stiffness data and the total equivalent mass. The calculation logic is to divide the real-time dynamic stiffness data by the total equivalent mass. Before performing the square root operation, it is necessary to ensure that the real-time dynamic stiffness data is converted into the international standard dimension in N / m. The square root operation is performed on the obtained ratio and divided by 2π for unit conversion. Thus, the actual natural frequency of the frame and main unit combination structure in the current state is obtained in Hz. In S702, the controller 12 reads the preset speed conversion coefficient and converts the actual natural frequency into the resonant critical speed. If the actual natural frequency is in Hz, the speed conversion coefficient can be 60 so that the resonant critical speed corresponds to rpm. In S703, the controller 12 collects the current operating speed of the rotating spindle 19, and calculates the difference between the operating speed and the resonance critical speed to obtain the real-time speed difference value. The smaller the absolute value of the real-time speed difference value, the closer the current excitation frequency is to the actual natural frequency of the machine base, and the higher the risk of resonance. The technical effect of this step is to convert the vibration transmission characteristics into a resonance critical speed that can be directly compared with the spindle speed, so that the controller 12 can continuously evaluate whether it is approaching the dangerous speed range under the condition that the equipment is running without stopping.

[0027] The main support frame 1 is also equipped with a speed control module 20. The rotating spindle 19 is controlled and adjusted by the speed control module 20, which is controlled by the controller 12. After step S703, the following steps are included: S801. Calculate the initial excitation energy based on the peak value of the top vibration acceleration; S802: Acquire the vibration electrical signals of the two acceleration sensors 11 and recalculate the real-time speed difference. Obtain the absolute value corresponding to the real-time speed difference as a safety margin feature. S803. Evaluate the safety status of the damping energy dissipation core 5 on the main load-bearing frame 1 based on the initial excitation energy and safety margin characteristics, and output the corresponding safety status results. This embodiment is used to evaluate the safety status of the damping energy dissipation core 5 in operation by combining the vibration excitation intensity and the degree of resonance proximity; the external machine equipment 4 is equipped with a rotating spindle 19, which is controlled by a controller 12. The main frame 1 is equipped with a speed regulation module 20, which is connected to the host drive system and is used to receive the speed regulation command issued by the controller 12. In S801, after completing S2 and obtaining the peak value of the top vibration acceleration, the controller 12 calculates the initial excitation energy based on the peak value of the top vibration acceleration. The initial excitation energy is used to characterize the vibration intensity of the host's current input frame. It can be calculated based on the peak value of the top vibration acceleration and the preset equivalent mass parameter, or based on the square of the peak value of the top vibration acceleration and the period parameter to calculate the relative energy index. Specifically, when using the relative energy index, the initial excitation energy... The calculation formula is: ; in, The extracted peak value of the top vibration acceleration. To set the duration of the period, This is a preset energy dimension conversion constant; the purpose is to form a unified excitation quantity that can be used for comparison; energy dimension conversion constant. The values ​​are obtained by calibrating the total equivalent mass of the system and the mode participation factor of the foundation on the experimental bench. Their dimensions are matched with the product of the square of the acceleration and time to ensure the excitation energy. The dimensions are correctly converted; it should be noted that the initial excitation energy E is an equivalent quantitative index used to characterize the relative magnitude of energy within the main vibration channel, not absolute physical mechanical energy; In S802, the controller 12 determines whether speed adjustment is needed based on the real-time speed difference or the resonance critical speed. When resonance needs to be avoided, the speed adjustment module 20 is controlled to work, so that the operating speed of the rotating spindle 19 is adjusted away from the resonance critical speed. After speed adjustment, the vibration electrical signals of the two acceleration sensors 11 are acquired, the vibration transmissibility, real-time dynamic stiffness and current speed difference are recalculated, and the absolute value of the speed difference is obtained. The complete calculation process for obtaining the absolute value of the speed difference is as follows: update the current actual natural frequency and new resonance critical speed of the frame using the real-time dynamic stiffness data obtained after speed adjustment, obtain the current real operating speed of the host fed back by the speed adjustment module 20, and take the absolute value of the difference between the real operating speed and the new resonance critical speed. In S803, the controller 12 evaluates the safety status of the damping energy dissipation core 5 based on the initial excitation energy and the absolute value of the speed difference. Since the spindle operating speed is higher or lower than the resonance critical speed, as long as the absolute value of the difference between the two is lower than the preset safety margin threshold, the excitation frequency of the host will fall into the resonance amplification frequency band of the machine base, causing the structural amplitude to exceed the safe amplitude range and high heat dissipation. Therefore, the absolute value of the speed difference is used as a unified frequency safety margin measurement index. The high excitation threshold and safety margin threshold are safety boundary values ​​pre-set based on the prototype durability test and resonance band sweep frequency test data of the warp knitting machine under different load conditions. The specific setting logic is as follows: take the vibration energy equivalent corresponding to the damping energy dissipation core reaching the maximum allowable steady-state temperature rise limit as the high excitation threshold; take 10% to 15% of the spindle speed value corresponding to the actual natural frequency as the safety margin threshold; when the initial excitation energy reaches the preset high excitation threshold and the absolute value of the speed difference is lower than the preset safety margin threshold, it indicates that the machine base is close to the resonance zone, the energy dissipation load borne by the damping energy dissipation core 5 increases, and the safety status evaluation result output is a warning level. When the initial excitation energy is lower than the high excitation threshold or the absolute value of the speed difference is higher than the safety margin threshold, it indicates that the working range of the damping energy dissipation core 5 is safe. This evaluation method enables the controller 12 to incorporate both the host excitation intensity and the structural frequency position into the judgment criteria, rather than making a judgment based solely on a single amplitude index, thereby improving the pertinence of identifying the operating status of the damping energy dissipation core 5. Specifically, the evaluation process in step S803 constitutes a two-dimensional judgment model for the safe state. The purpose of this model is to comprehensively assess whether the damping energy dissipation core 5 faces the risk of overload damage or resonance failure during the variable speed operation of the warp knitting machine. In terms of logic structure and data flow, the model receives the initial excitation energy as the first dimension data reflecting the external load input, and at the same time receives the absolute value of the speed difference as the second dimension data reflecting the system frequency safety margin. The model inputs the data of these two dimensions into the preset two-dimensional judgment logic matrix, and outputs the final safety state through matrix mapping. In terms of the physical relationship represented, the model abstracts the nonlinear superposition law of external excitation energy input and structural dynamic response in the resonance amplification range. Because when the excitation energy is high and the frequency is close to the resonance region, the stress amplitude and heat dissipation inside the material will increase sharply. Therefore, the model can accurately reveal the real physical load boundary of the damping energy dissipation core 5 under complex working conditions by making joint judgments of the above two dimensions. In this embodiment, the initial excitation energy is preferably used as a relative evaluation index. Its logical function is not to obtain the absolute mechanical energy value, but to normalize the excitation strength at different operating times into the same judgment system. In specific processing, the controller 12 first obtains the peak value of the top vibration acceleration within a continuously set time window. The time window is preferably consistent with the peak value extraction time window. Combining the equivalent mass parameters and period parameters stored in the installation and commissioning phase, the peak value of the top vibration acceleration is converted into the initial excitation energy level, or it is directly divided into three levels of low excitation, medium excitation and high excitation according to the preset grading boundary. The reason for adopting the grading process is that the key to judging the safety status of the damping energy dissipation core 5 is to compare the excitation level, rather than having to obtain a complex absolute energy formula. The absolute value of the speed difference in S802 is used to characterize the distance between the current spindle operating point and the resonance critical speed, and its physical meaning is the frequency safety margin. After receiving the instruction from the controller 12, the speed regulation module 20 can gradually increase or decrease the speed according to the preset step size. After each speed regulation, it maintains a short period of stability and then re-acquires the top and bottom acceleration vibration electrical signals. The controller 12 repeatedly performs the calculation of vibration transmissibility, real-time attenuation rate and real-time dynamic stiffness on the data after speed regulation, and updates the absolute value of the speed difference in combination with the resonance critical speed. If the absolute value of the speed difference increases and the peak value of the top vibration acceleration decreases, the controller 12 determines that the current speed adjustment direction is valid; if the absolute value of the speed difference does not increase or the peak value of the top vibration acceleration increases instead, the controller 12 can stop the current speed adjustment direction and try another direction, thereby ensuring that there is a clear data closed loop between the speed adjustment action and the vibration feedback. The safety status evaluation in S803 preferably adopts a two-dimensional judgment logic: first, the initial excitation energy reflects the current input load level of the damping energy dissipation core 5; second, the absolute value of the speed difference reflects whether the load is located at a dangerous frequency position close to resonance. The controller 12 can pre-establish a safety status judgment table. When the initial excitation energy is at the high excitation level and the absolute value of the speed difference is in the small margin range, it is evaluated as a high-risk warning state; when the initial excitation energy is at the medium excitation level and the absolute value of the speed difference is in the medium margin range, it is evaluated as a state of concern. When the initial excitation energy is at a low excitation level or the absolute value of the speed difference is in a large margin range, it is evaluated as a safe state; when the initial excitation energy is at a high excitation level and the absolute value of the speed difference is in a medium margin range, or when the initial excitation energy is at a medium excitation level and the absolute value of the speed difference is in a small margin range, it is evaluated as a state of concern. The boundaries of each gear position are preferably calibrated based on the vibration peak value, temperature rise of damping energy dissipation core 5, running time and disassembly and inspection results recorded in the prototype test, so that the safety status evaluation can correspond to the actual damage risk. Through this gearing and judgment table method, the safety status of damping energy dissipation core 5 is no longer an abstract conclusion, but is derived from the collectable top vibration acceleration peak value and the calculable absolute value of the speed difference, and is directly used as the judgment input for subsequent speed limit, alarm or shutdown protection. To enable the above two-dimensional decision logic to be directly implemented in the software module, a specific example of decision matrix flow is provided here: the controller 12 internally stores a three-by-three safety state decision matrix; its row index corresponds to the level of the initial excitation energy, such as low excitation, medium excitation and high excitation; its column index corresponds to the level of the absolute value of the speed difference, such as large margin, medium margin and small margin. Assuming that at the current moment, the controller 12 calculates that the initial excitation energy falls into the middle excitation row and the absolute value of the speed difference falls into the smaller margin column, the controller 12 directly locates the corresponding cross cell of the matrix through the lookup table logic. The preset state value of this cell is the state of interest. The controller 12 then sends the status value as an output to the human-machine interface for prompting, or triggers the subsequent speed limit protection program. This lookup table method does not require complex nonlinear formula calculations, and can realize the automatic interaction and fusion of two dimensions of data: excitation input and frequency margin, which meets the requirements of the industrial controller 12 for real-time operation and logical clarity.

[0028] The embodiments of this application have been described above with reference to the accompanying drawings. However, this application is not limited to the specific embodiments described above. The specific embodiments described above are merely illustrative and not restrictive. Those skilled in the art can make many other forms under the guidance of this application without departing from the spirit and scope of the claims, and all of these forms are within the protection scope of this application.

Claims

1. A high-stability support base for a warp knitting machine, characterized in that, include: The main support frame (1) is provided with an upper mounting plate (2) on top. The internal structure of the main support frame (1) has a damping filling cavity (3). The upper mounting plate (2) is used to fix external machinery and equipment (4). The damping energy dissipation core (5) is densely filled into the damping filling cavity (3); The leveling support foot (6) is connected to the bottom of the main support frame (1), and the bottom end of the leveling support foot (6) is provided with a hemispherical protrusion (7). A spherical adaptive pad (8) is placed on the ground. The upper surface of the spherical adaptive pad (8) is provided with a hemispherical groove (9) that matches the hemispherical protrusion (7). The hemispherical protrusion (7) is located in the hemispherical groove (9) to form a spherical contact fit. Two monitoring units (10) are respectively installed on the upper mounting plate (2) and the spherical adaptive pad (8). Each monitoring unit (10) is provided with an acceleration sensor (11). The two acceleration sensors (11) are respectively used to acquire a first vibration electrical signal characterizing the top vibration acceleration in the vertical direction and a second vibration electrical signal characterizing the bottom vibration acceleration in the vertical direction. The controller (12) is electrically connected to the two acceleration sensors (11) for receiving vibration electrical signals and controlling the acceleration sensors (11).

2. The high-stability support frame for warp knitting machines according to claim 1, characterized in that, The main support frame (1) is a hollow square steel column (13) with a wall thickness of 10mm. The cross-sectional dimensions of the hollow square steel column (13) are 200mm×200mm. The upper mounting plate (2) has through holes (14) for fixing external machinery and equipment (4) with bolts (15).

3. The high-stability support frame for warp knitting machines according to claim 2, characterized in that, The bottom end face of the main support frame (1) is fixedly connected to a base plate (16), and the center of the base plate (16) is machined with an internal thread hole (17). The top end of the leveling support foot (6) is a screw (18), and the screw (18) is screwed into the internal thread hole (17).

4. The high-stability support frame for warp knitting machines according to claim 1, characterized in that, The damping energy dissipation core (5) is composed of a mixture of epoxy resin and quartz sand with a volume ratio of 1:3, which is then cured.

5. The high-stability support frame for a warp knitting machine according to any one of claims 1 to 4, characterized in that, The surfaces of the hemispherical protrusion (7) and the hemispherical groove (9) are both hardened and coated with molybdenum disulfide grease (21).

6. The high-stability support frame for a warp knitting machine according to any one of claims 1 to 4, characterized in that, The combination of the hemispherical protrusion (7) and the hemispherical groove (9) allows the leveling support foot (6) to deflect freely within a spatial cone angle range of ±5 degrees.

7. A method for a high-stability support frame for a warp knitting machine, applied to the high-stability support frame for a warp knitting machine as described in claim 1, characterized in that, include: S1. Real-time acquisition of the first vibration electrical signal of the acceleration sensor (11) on the upper mounting plate (2), and calculation of the peak value of the top vibration acceleration; S2. Obtain the second vibration electrical signal of the acceleration sensor (11) on the spherical adaptive pad (8), and calculate the peak value of the bottom vibration acceleration; S3. Based on the peak value of the bottom vibration acceleration and the peak value of the top vibration acceleration, and combined with the preset structural equivalent stiffness coefficient, real-time dynamic stiffness data is obtained. S4. Based on the real-time dynamic stiffness data, conduct a safety assessment of the aging state of the damping energy dissipation core (5) or the resonance risk of the bearing base.

8. The method for a high-stability support base for a warp knitting machine according to claim 7, characterized in that, In step S4, based on the real-time dynamic stiffness data, a safety assessment is performed on the aging state of the damping energy dissipation core (5), specifically including: S601. Obtain the standard dynamic stiffness under the initial installation state, and obtain the stiffness difference based on the standard dynamic stiffness and the real-time dynamic stiffness data; S602. Obtain a preset time interval and obtain average degradation data based on the stiffness difference over a continuous time period. S603. Based on the stiffness difference and the average degradation data, obtain the aging score of the damping energy dissipation core (5) and output the aging warning status based on the preset aging threshold range.

9. The method for a high-stability support base for a warp knitting machine according to claim 7, characterized in that, In step S4, based on the real-time dynamic stiffness data, a safety assessment is performed on the resonance risk of the bearing base, specifically including: S701. Obtain the total equivalent mass of the bearing base and external machine equipment (4) in real time, and calculate the actual natural frequency based on the real-time dynamic stiffness data. S702. Obtain a preset rotational speed conversion coefficient and convert the actual natural frequency to obtain the resonance critical rotational speed; S703. The current operating speed of the rotating spindle (19) inside the external machine equipment (4) is obtained in real time, and the real-time speed difference is obtained based on the operating speed and the resonance critical speed.

10. The method for a high-stability support base for a warp knitting machine according to claim 9, characterized in that, The main support frame (1) is also equipped with a speed regulation module (20). The rotating spindle (19) is controlled and adjusted by the speed regulation module (20) controlled by the controller (12). After step S703, the following steps are included: S801. Calculate the initial excitation energy based on the peak value of the top vibration acceleration; S802. Obtain the vibration electrical signals of the two acceleration sensors (11) and recalculate the real-time speed difference, and then obtain the absolute value corresponding to the real-time speed difference as a safety margin feature. S803. Evaluate the safety status of the damping energy dissipation core (5) on the main support frame (1) based on the initial excitation energy and the safety margin characteristics, and output the corresponding safety status results.

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